JP2007285362A - Valve device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a valve device capable of reducing " fluid reaction (valve closing force) " acting on a ball valve in a microscopic valve opening range, without reducing a dimension in the radial direction of a tapered slide. <P>SOLUTION: This valve device has a plurality of recessed parts 34 in the peripheral direction of the tapered slide 31, and reduces a rate of a microscopic clearance formed between the ball valve 4 and the tapered slide 31 even in the microscopic valve opening range". The fluid reaction " acting on the ball valve 4 reduces by reducing the rate of the microscopic clearance, and valve opening force in the microscopic valve opening range can be reduced. Since "the fluid reaction" can be reduced by arranging the recessed parts 34, there is no need to reduce the dimension in the radial direction of the tapered slide 31. Thus, when closing the valve, the ball valve 4 can be surely guided to a seating seat 32 by the tapered slide 31, and a distance between the seating seat 32 and a port side edge part 33 can be secured, and valve leakage can be prevented even if abrasion and deformation are caused in the port side edge part 33. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to a valve device having a structure in which a valve element is seated on a seating seat of a taper slide in a state where the valve element is disposed on the fluid supply side with respect to a seat portion and the valve element overlaps the taper slide in the axial direction.

(Conventional technology)
As an example of this type of valve device, valve devices disclosed in Patent Documents 1 and 2 are known.
The valve device of Patent Documents 1 and 2 will be described with reference to FIG. 9A. A seat portion J2 in which a valve opening J1 through which oil (an example of a fluid) can pass is formed, and the oil is more oil than the seat portion J2. A ball valve (an example of a valve body) J3 disposed on the supply side and capable of opening and closing the valve opening J1, and an electromagnetic actuator (an example of a valve driving means: an example of a valve driving means: FIG. 9) that can drive the ball valve J3 in the valve opening direction. (Not shown).

The seat portion J2 on which the ball valve J3 is seated has a shape expanding toward the fluid supply side around the valve opening J1, and a taper slide (taper guide) J5 for guiding the ball valve J3 to the seating seat J4. Is formed. The inner diameter of the taper slide J5 is the mouth edge J6 of the valve opening J1, and the seating seat J4 that comes into contact with the ball valve J3 is formed on the outer circumference side of the mouth edge J6.
Here, a radial clearance for sliding the ball valve J3 is provided between the ball valve J3 and a radial member (such as a ball guide). This radial clearance is large enough to compensate for axial misalignment during component assembly.
For this reason, the outer diameter of the taper slide J5 is set large for the purpose of reliably guiding the ball valve J3 moving in the radial direction with the radial clearance set to be large into the taper slide J5.

(Problems of conventional technology)
The ball valve J3 receives a hydraulic load (hereinafter referred to as a static pressure-receiving load) based on a differential pressure between the hydraulic pressure supplied from the input port and the low pressure on the valve opening J1 side. The static pressure-receiving load is the valve closing force (force in the seating direction) of the ball valve J3.
For this reason, when opening the valve opening J1, the electromagnetic actuator generates a valve opening force that overcomes the “static pressure load (valve closing force)” applied to the ball valve J3 in addition to the “spring load” of the return spring. There is a need to.

When the ball valve J3 is separated from the seating seat J4, as shown by an arrow α in FIG. 9B, high-speed oil passes through a minute gap between the ball valve J3 and the taper slide J5. Since the oil flow direction in the minute gap is in the valve closing direction in the axial direction, “fluid reaction force (see arrow β in the figure)” in which the oil in the high-speed flow in the minute gap becomes the valve closing force on the ball valve J3. Will be given.
For this reason, the electromagnetic actuator opens over the “fluid reaction force (valve closing force)” in addition to the “spring load” and “static pressure receiving load (valve closing force)” of the return spring in the minute valve opening range. Need to generate power.

The electromagnetic actuator is required to save power, but it is necessary to generate a valve opening force that overcomes the “fluid reaction force” in the minute valve opening range.
In particular, in recent years, there is an environment in which high-pressure specifications of the supply hydraulic pressure have been advanced, and the “fluid reaction force” increases as the pressure increases, so the power consumption of the electromagnetic actuator tends to increase.

Note that the “fluid reaction force” can be reduced by reducing the radial dimension of the taper slide J5 and bringing the taper slide J5 closer to a pin-angle shape.
However, as described above, since a large radial clearance is provided between the ball valve J3 and the radial member (ball guide or the like), if the radial dimension of the taper slide J5 is reduced, the ball valve J3 is closed when the valve is closed. May not be guided into the taper slide J5 and a valve closing operation failure may occur, and reliability is impaired.
Further, by reducing the radial dimension of the taper slide J5, when the seating seat J4 and the mouth edge portion J6 approach each other, high-speed oil flows through the mouth edge portion J6. The deformation easily reaches the seating seat J4, and valve leakage may occur when the valve is closed, and reliability is impaired.
JP 2004-286097 A JP 2002-286152 A JP-A-5-5470 JP 60-4679 A

  The present invention has been made in view of the above problems, and its object is to reduce the “fluid reaction force” acting on the valve body in the minute valve opening range without reducing the radial dimension of the taper slide. To provide a valve device.

[Means of claim 1]
The taper slide of the valve device employing the means of claim 1 includes a plurality of recesses recessed in the axial direction on the outer diameter side of the seating seat in the circumferential direction.
For this reason, even in the minute valve opening range, the proportion of minute gaps formed between the valve element and the taper slide is reduced by the plurality of recesses. Since a large “fluid reaction force” is generated by the minute gap, the “fluid reaction force” acting on the valve body is reduced by reducing the proportion of the minute gap.
As described above, since the “fluid reaction force” can be reduced by providing a plurality of recesses in the taper slide without reducing the radial dimension of the taper slide, the valve opening force required for the valve driving means in the minute valve opening range. Can be reduced.

[Means of claim 2]
The valve body of the valve device adopting the means of claim 2 is a ball valve in which the portion seated on the seat is a spherical valve.
Thereby, in the valve device using the ball valve, the valve opening force in the minute valve opening range can be reduced without reducing the radial dimension of the taper slide.
In addition, since the radial dimension of the taper slide can be secured sufficiently, the occurrence of valve closing malfunctions is prevented, and wear and deformation at the edge of the mouth are difficult to reach the seating seat, preventing valve leakage during valve closing. it can.

[Means of claim 3]
The recess of the valve device employing the means of claim 3 is a groove extending in the radial direction or a local depression.

[Means of claim 4]
The concave portion of the valve device employing the means of claim 4 is provided so as to guide the fluid flowing into the concave portion in the inner diameter direction, and the side close to the seating seat of the concave portion serves as a shaft for the fluid guided in the inner diameter direction by the concave portion. It is an inclined surface that is directed toward the fluid supply side.
Thereby, the fluid that has flowed into the recess in the minute valve opening range flows to the fluid supply side (the valve opening direction) by the inclined surface, and gives a force in the valve opening direction (hereinafter referred to as a separation force) to the valve body.
Since this separation force acts so as to cancel out the “fluid reaction force” acting on the valve body, the valve opening force required for the valve driving means in the minute valve opening range can be further reduced.

[Means of claim 5]
The inclined surface of the valve device employing the means of claim 5 is a curved surface.
Thereby, after flowing into the recess, the flow of the fluid flowing toward the fluid supply side (valve opening direction) can be made smooth, and the separating force can be efficiently generated by the recess.

[Means of claim 6]
The seat portion of the valve device employing the means of claim 6 is a resin molded product obtained by molding a resin material with a molding die.
For this reason, a several recessed part can be easily formed in a sheet | seat part, and the raise of the cost of a sheet | seat part can be prevented. That is, it is possible to provide a highly reliable valve device in which a recess is formed without causing an increase in cost.

[Means of Claim 7]
The valve body of the valve device adopting the means of claim 7 is a valve body having an axisymmetric shape having a conical shape or an arbitrary curved surface shape that partially overlaps the seat portion in the axial direction when seated on the seat. It is. And a some recessed part is provided in the surface facing a taper slide and an axial direction among valve bodies instead of a taper slide.
The effect of the concave portion described in claims 1 to 6 can be obtained in the same manner even if it is provided not only on the fixed side seat portion but also on the movable side valve body. That is, the effect of reducing the fluid reaction force and the effect of generating the separation force can also be obtained by the plurality of recesses provided in the valve body.
In addition, by providing a plurality of concave portions in both the fixed-side seat portion and the movable-side valve body, the fluid reaction force can be reduced more efficiently or the separation force can be increased.

[Means of Claim 8]
A valve body (valve body provided with a recess) of the valve device employing the means of claim 8 is a resin molded product obtained by molding a resin material with a molding die.
For this reason, a several recessed part can be easily formed in the surface of a valve body, and the raise of the cost of a valve body can be prevented. That is, it is possible to provide a highly reliable valve device in which a recess is formed without causing an increase in cost.

[Means of claim 9]
The valve drive means of the valve device employing the means of claim 9 is an electromagnetic actuator that generates a valve opening force in accordance with the energization amount.
For this reason, the valve opening force required for the electromagnetic actuator in the minute valve opening range can be reduced, and the power consumption of the electromagnetic actuator in the minute valve opening range can be suppressed.

The valve device of the best mode 1 has a valve opening through which a fluid can pass, and a seat part provided with a taper slide provided around the valve opening and extending toward the fluid supply side, and the seat part. Is provided on the fluid supply side, and includes a valve body capable of opening and closing the valve opening, and valve driving means capable of driving the valve body in the valve opening direction.
This valve device has a structure in which the valve body is seated on the seating seat of the taper slide in a state where the valve body overlaps the taper slide in the axial direction, and the taper slide is arranged in the axial direction on the outer diameter side of the seating seat. A plurality of recessed recesses are provided in the circumferential direction.

  A first embodiment in which the valve device of the present invention is applied to a three-way solenoid valve (an example of a valve device) that controls hydraulic pressure or oil flow rate will be described. In the first embodiment, the “basic structure of the three-way solenoid valve” will be described first, and then the “features of the first embodiment” will be described.

[Basic structure of three-way solenoid valve]
First, the basic structure of the three-way solenoid valve will be described with reference to FIG.
The three-way solenoid valve is a normally closed (N / C) type electromagnetic hydraulic control valve that is assembled in a hydraulic controller that performs hydraulic control, for example, in an automatic transmission of an automobile. The three-way valve 1 and the three-way valve 1 are driven. And an electromagnetic actuator 2 (an example of a valve driving means).

(Description of three-way valve 1)
The three-way valve 1 includes a valve housing (valve base) 3, a ball valve 4, a shaft 5, and a return spring 6.
The valve housing 3 has a substantially cylindrical shape, and communicates with an oil pump (not shown) through a switching valve, an oil passage, and the like, and an input port 11 to which oil (an example of fluid) discharged from the oil pump is supplied. And an output port 12 that communicates with a hydraulic actuator (hydraulic servo chamber) of a friction engagement device (automatic transmission clutch, brake, etc.) via an oil passage, and a discharge port 13 that communicates with the oil pan. .
The input port 11 is provided at the end of the valve housing 3 (left end in FIG. 3), and the output port 12 and the discharge port 13 are provided in the radial direction of the valve housing 3.

The interior of the valve housing 3 is divided into an input chamber 14 that communicates with the input port 11, an output chamber 15 that communicates with the output port 12, and a discharge chamber 16 that communicates with the discharge port 13. An input chamber 14, an output chamber 15, and a discharge chamber 16 are arranged toward the front.
The input chamber 14 and the output chamber 15 are partitioned by an input side partition wall 17, and the output chamber 15 and the discharge chamber 16 are partitioned by a discharge side partition wall 18.
In the center of the input side partition wall 17, an input valve port 21 that communicates the input chamber 14 and the output chamber 15 is provided. The input-side partition wall 17 corresponds to a seat portion, the input valve port 21 corresponds to a valve opening, and the technology around the input valve port 21 will be described later.
On the other hand, a discharge valve port 22 that communicates the output chamber 15 and the discharge chamber 16 is also provided at the center of the discharge-side partition wall 18. The input valve port 21 and the discharge valve port 22 are both provided on the axis of the shaft 5.

The ball valve 4 is disposed in the input chamber 14 and closes the input valve port 21 by the hydraulic pressure supplied from the input port 11 into the input chamber 14. The ball valve 4 is inserted into the input chamber 14 from the tip of the valve housing 3. The ball valve 4 is held in the vicinity of the input valve port 21 by the assembled ball guide 23.
The ball guide 23 supports the ball valve 4 so as to be movable within a predetermined valve opening direction from a position where the input valve port 21 is closed, and between the ball guide 23 and the ball valve 4 in the radial direction, A radial clearance for sliding the ball valve 4 is provided. This radial clearance is provided with a sufficient size so as to compensate for the axial deviation when assembling the parts.

The shaft 5 includes a pressing shaft 25, a medium diameter shaft 26, and a large diameter shaft 27 from the left side in FIG. 3 (input chamber 14 side) to the right side in FIG. 3.
The pressing shaft 25 is provided at the left end of the shaft 5 in FIG. 3 and has a smaller diameter than the input valve port 21 and the discharge valve port 22, and is inserted into the input valve port 21 from the output chamber 15 side to be a ball valve. 4 can be displaced in the valve opening direction.
The medium diameter shaft 26 is provided with a slightly larger diameter than the pressing shaft 25, and moves in the axial direction in the discharge chamber 16.
A step valve 28 that can close the discharge valve port 22 from the discharge chamber 16 side is provided at the step between the pressing shaft 25 and the medium diameter shaft 26. That is, the shaft 5 includes a step valve 28 at an intermediate position in the axial direction.
The large-diameter shaft 27 is provided with a slightly larger diameter than the medium-diameter shaft 26 and is supported by the inner peripheral surface of a sleeve 29 supported in the electromagnetic actuator 2 so as to be slidable in the axial direction.

  The return spring 6 is a compression coil spring that urges the shaft 5 toward the electromagnetic actuator 2. The return spring 6 is supported in the discharge chamber 16 and serves also to support the shaft 5, and a step (middle of the large diameter shaft 27). Between the radial shaft 26 and the large-diameter shaft 27). As a result, the shaft 5 is urged to the right in FIG. 3 by the return spring 6.

(Description of electromagnetic actuator 2)
The electromagnetic actuator 2 has a known structure including a coil, a moving core, a stator, a yoke, and the like, and a valve opening force toward the left in FIG. 3 is applied to the moving core in accordance with the amount of current applied to the coil. The axial opening force of the moving core is given to the shaft 5, and the moving core drives the shaft 5 in the left direction in FIG. 3 as the energization amount given to the coil increases.

[Features of Example 1]
As described above, the radial direction between the ball guide 23 and the ball valve 4 has a sufficient radial direction for the purpose of sliding the ball valve 4 and for the purpose of compensating for shaft misalignment when assembling the parts. Clearance is provided.
Therefore, as shown in FIG. 1, the ball valve 4 is guided to the input valve port 21 when the valve is closed, even if the ball valve 4 is displaced in the radial direction by the radial clearance during the valve opening. A taper slide 31 is formed. The taper slide 31 is a funnel surface that is provided around the input valve port 21 and has a conical shape that expands toward the oil supply side. Further, the outer diameter of the taper slide 31 is large so that the ball valve 4 that moves in the radial direction with a large radial clearance is surely guided into the taper slide 31.

The ball valve 4 is seated on the taper slide 31 to close the input valve port 21, and a seating seat 32, which is a portion on which the ball valve 4 is seated, exists in an annular shape on the taper slide 31.
On the other hand, the inner peripheral diameter of the taper slide 31 is a mouth edge portion (an axial edge portion on the oil supply side of the input valve port 21) 33 of the input valve port 21. The mouth edge portion 33 has a corner in cross section, and wear and deformation occur as high-speed oil flows repeatedly over a long period of time. For this reason, the diameter of the seating sheet 32 is set so that the wear or deformation does not reach the seating sheet 32 even if the mouth edge portion 33 is worn or deformed. That is, as shown in FIG. 1A, the seat diameter of the seating seat 32 is set to be separated from the mouth edge portion 33 to the outer diameter side by a predetermined amount in anticipation of wear and deformation.

The taper slide 31 includes a plurality of recesses 34 that are recessed in the axial direction on the outer diameter side of the seating seat 32 in the circumferential direction. The concave portion 34 is formed between the ball valve 4 and the taper slide 31 by increasing a clearance distance between the ball valve 4 and the bottom of the concave portion 34 at the position of the concave portion 34 when the ball valve 4 is separated by a minute amount. This is a means for reducing the ratio of the formed minute gaps.
Specifically, the recesses 34 of the first embodiment are grooves extending in the radial direction as shown in FIG. 1A, and three recesses 34 are provided at equal intervals in the circumferential direction of the taper slide 31. In addition, the number of the recessed parts 34 can be set suitably.
The groove width of the recess 34 can be appropriately set within a range that does not hinder the ball valve 4 from being guided to the seating seat 32.
The inner peripheral end (end closer to the seating seat 32) of the recess 34 is provided on the outer diameter side of the seating seat 32, and is provided so that valve leakage does not occur through the recess 34.
The outer peripheral end of the recess 34 is not particularly defined and can be set as appropriate.

The shape of the recessed part 34 in Example 1 is demonstrated.
As shown in FIG. 1B, the bottom of the recess 34 is a substantially flat surface extending in a direction perpendicular to the axial direction.
The wall surface (surface around the bottom surface) of the recess 34 is formed along the axial direction over the entire circumference, and the inclined surface 34a shown in the second and subsequent embodiments is not formed.

(Effect 1 of Example 1)
The three-way solenoid valve according to the first embodiment includes a plurality of recesses 34 in the circumferential direction of the taper slide 31, so that a minute gap formed between the ball valve 4 and the taper slide 31 even in the minute valve opening range. Is reduced by the plurality of recesses 34.
Since a large “fluid reaction force” is generated by the minute gap, the “fluid reaction force” acting on the ball valve 4 is reduced by reducing the proportion of the minute gap.
Thus, since the “fluid reaction force” acting on the ball valve 4 in the minute valve opening range can be reduced, the valve opening force in the minute valve opening range can be lowered, and the power consumption of the electromagnetic actuator 2 in the minute valve opening range. Can be lowered.

This effect will be specifically described.
In a range where the ball valve 4 is separated from the seating seat 32 by a minute amount, the ball valve 4 and the taper slide 31 overlap in the axial direction, and oil passes through the minute gap between the ball valve 4 and the taper slide 31 at a high speed. To do. Since the flow direction of this high-speed flow oil is directed in the valve closing direction in the axial direction, the high-speed flow oil flowing through the minute gap gives a “fluid reaction force” to the ball valve 4.

Here, for comparison, a three-way solenoid valve to which the present invention is not applied (that is, no recess 34) will be described as an example. A minute gap is formed in the entire circumferential direction of the taper slide 31 in the minute valve opening range. Therefore, as shown by the solid line A in FIG. 2A, the “fluid reaction force” acting on the ball valve 4 increases.
For this reason, the electromagnetic actuator 2 is required to have a valve opening force that overcomes the “large fluid reaction force” in the minute valve opening range, and the solid line B in FIG. 2B in the “maximum value of the fluid reaction force”. As shown in FIG. 2, the operating voltage of the electromagnetic actuator 2 becomes large.

On the other hand, in the case of the three-way solenoid valve according to the first embodiment to which the present invention is applied, the ratio of the minute gaps is reduced by the plurality of recesses 34 provided in the circumferential direction of the taper slide 31, so that the dashed line C in FIG. As shown, the “fluid reaction force” acting on the ball valve 4 is reduced.
As described above, since the “fluid reaction force” can be reduced in the first embodiment, the valve opening force required for the electromagnetic actuator 2 in the minute valve opening range is reduced, and the “maximum value of the fluid reaction force” in FIG. As shown by the solid line D, the operating voltage of the electromagnetic actuator 2 can be reduced, and power saving of the electromagnetic actuator 2 can be achieved.
In addition, the broken line E shown to Fig.2 (a) shows a static pressure receiving load.

Further, in recent years, there has been an environment in which high-pressure specifications of the supply hydraulic pressure are progressing, and the “fluid reaction force” increases as the pressure increases, so that the electromagnetic actuator 2 tends to become larger and the power consumption tends to increase.
However, since the three-way solenoid valve of the first embodiment can suppress the “fluid reaction force” as described above, the valve opening force required for the electromagnetic actuator 2 can be suppressed even when the supply pressure is increased. It is possible to avoid the enlargement of the electromagnetic actuator 2 and the deterioration of power consumption.

(Effect 2 of Example 1)
In the first embodiment, the “fluid reaction force” is reduced by providing the recess 34, and it is not necessary to reduce the radial dimension of the taper slide 31. For this reason, the radial dimension of the taper slide 31 can be sufficiently secured. Accordingly, the ball valve 4 can be reliably guided to the seating seat 32 by the taper slide 31 when the valve is closed, the occurrence of valve closing operation failure can be prevented, and the reliability of the three-way solenoid valve is not impaired.
Further, since the radial dimension of the taper slide 31 can be sufficiently ensured, the necessary radial distance between the seating seat 32 and the mouth edge portion 33 can be easily ensured. As a result, even if wear or deformation occurs in the mouth edge portion 33 due to long-term use, the wear or deformation does not easily reach the seating seat 32, and valve leakage at the time of valve closing can be prevented. There is no loss of reliability.

(Effect 3 of Example 1)
The input side partition wall 17 in which at least the recess 34 is formed is a resin molded product obtained by molding a resin material with a molding die. For this reason, the plurality of recesses 34 can be easily formed in the input side partition wall 17, and an increase in cost due to the provision of the plurality of recesses 34 can be prevented. That is, a highly reliable three-way solenoid valve in which the recess 34 is formed can be provided without causing an increase in cost.

A second embodiment will be described with reference to FIG. In the following embodiments, the same reference numerals as those in the first embodiment denote the same functions.
The recessed part 34 of Example 2 is provided to guide the fluid flowing into the recessed part 34 in the inner diameter direction. Specifically, the bottom of the concave portion 34 is inclined substantially along the axial inclination of the taper slide 31, and is provided so that oil flowing into the concave portion 34 when opening the valve is directed toward the inner diameter direction efficiently.

Further, the side of the recess 34 close to the seating seat 32 is provided with an inclined surface 34a that directs the oil guided in the inner diameter direction toward the fluid supply side in the axial direction, and flows into the recess 34 in the minute valve opening range. Oil is struck against the ball valve 4 (see the arrow in FIG. 4), and the ball valve 4 is given a separating force in the valve opening direction.
This separation force acts so as to cancel out the “fluid reaction force” acting on the ball valve 4, so that the valve opening force in the minute valve opening range can be further reduced, and the operating voltage of the electromagnetic actuator 2 in the minute valve opening range. Can be further suppressed than in the first embodiment.

A third embodiment will be described with reference to FIG.
The recessed part 34 of Example 3 is provided in the curved surface where the inclined surface 34a near the seating seat 32 is curved in an arc shape.
Thus, by providing the side close to the seating seat 32 on the curved surface, the oil that has flowed into the recess 34 in the minute valve opening range can be smoothly hit the ball valve 4 (see the arrow in FIG. 5). That is, the flow efficiency of the oil directed in the valve opening direction by the concave portion 34 can be increased, and the separating force can be efficiently generated by the concave portion 34. As a result, the valve opening force in the minute valve opening range can be further reduced, and the operating voltage of the electromagnetic actuator 2 can be further reduced as compared with the second embodiment.

A fourth embodiment will be described with reference to FIG.
In the second and third embodiments, the example in which the bottom of the recess 34 is inclined substantially along the inclination of the taper slide 31 in the axial direction has been described.
On the other hand, the recess 34 of the fourth embodiment is provided in a rectangular recess having substantially the same vertical and horizontal width when viewed from the input chamber 14 side.

A fifth embodiment will be described with reference to FIG.
The concave portion 34 of the fifth embodiment is provided in a substantially circular depression as seen from the input chamber 14 side {see FIG. 7A}, and the bottom of the concave portion 34 is also provided on a spherical curved surface. It is.

[Modification]
In the first to third embodiments, the recess 34 is provided in a groove shape, and in the fourth and fifth embodiments, the recess 34 is provided in a recess having substantially the same vertical and horizontal width when viewed from the fluid supply side. And may be used in combination. Moreover, the number and shape of the recessed part 34 are not limited to the thing of Examples 1-5, It can change variously.

In the above embodiment, the ball valve 4 is disclosed as an example of the valve body. However, at least when the valve body and the taper slide 31 overlap in the axial direction at the time of minute opening, any valve may be used, such as a pivot valve (conical valve) or the like. The present invention may be applied to a valve device having a valve body of another shape.
Further, as shown in FIG. 8 as Example 6, when the valve body 4a exhibits an axisymmetric shape having a conical shape or an arbitrary curved surface shape, the plurality of recesses 34 provided in the taper slide 31 in the above example are You may provide in the surface 31a of the valve body 4a facing the taper slide 31 in an axial direction. As described above, the effect of the concave portion 34 described in the above embodiment can be obtained in the same manner not only in the fixed side taper slide 31 but also in the movable side valve body 4a. That is, the effect of reducing the fluid reaction force and the effect of generating the separation force can also be obtained by the plurality of recesses 34 provided in the valve body 4a.
In addition, by providing the plurality of recesses 34 in both the fixed-side taper slide 31 and the movable-side valve body 4a, the fluid reaction force can be reduced more efficiently and the separation force can be increased.

In the above embodiment, an example in which the input side partition wall 17 corresponding to the sheet portion is a resin molded product is shown. However, even if the input side partition wall 17 is provided by using a forging technique, the cost increases due to the provision of the plurality of recesses 34. Can be prevented. Further, as shown in the sixth embodiment, even when a plurality of recesses 34 are provided in the valve body 4a, the valve body 4a may be formed by using a resin molded product or by using a forging technique. Further, the recess 34 may be provided by a technique such as cutting.
In the above embodiment, the present invention is applied to a valve device having a three-way valve structure. However, the present invention is applied to valve devices having other structures such as a two-way valve (open / close valve) structure and a four-way valve structure. May be.
In the above embodiment, the electromagnetic actuator 2 is used as the valve driving means. However, other actuators such as a piezoelectric actuator may be used.
In the above embodiment, the example in which the present invention is applied to the valve device used in the hydraulic controller of the automatic transmission has been shown. However, the present invention may be applied to a valve device other than the automatic transmission.

It is the valve opening periphery view seen from the oil supply side, and the principal part sectional drawing of a valve apparatus (Example 1). It is a graph for operation | movement description (Example 1). (Example 1) which is principal part sectional drawing in alignment with the axial direction of a three-way solenoid valve. It is the valve opening periphery view seen from the oil supply side, and the principal part sectional drawing of a valve apparatus (Example 2). (Example 3) which is the valve opening periphery view seen from the oil supply side, and the principal part sectional drawing of a valve apparatus. It is principal part sectional drawing of a valve apparatus (Example 4). (Example 5) which is the principal part enlarged view of the taper slide seen from the oil supply side, and the principal part sectional drawing of a valve apparatus. FIG. 10 is a view of the valve body as seen from a side different from the oil supply side, and a cross-sectional view of the main part of the valve device (Example 6). It is principal part sectional drawing of a valve apparatus (conventional example).

Explanation of symbols

1 Three-way valve 2 Electromagnetic actuator (valve drive means)
4 Ball valve (valve)
4a Valve body 17 Input-side partition (seat part)
21 Input valve port (valve opening)
31 Tapered slide 32 Seating seat 33 Mouth edge 34 Recess 34a Inclined surface

Claims (9)

A seat having a valve opening through which a fluid can pass, and a taper slide provided around the valve opening and having a shape spreading toward the fluid supply side;
A valve body that is disposed on the fluid supply side of the seat portion and can open and close the valve opening;
In a valve device comprising valve drive means capable of driving the valve body in the valve opening direction,
This valve device has a structure in which the valve body is seated on a seating seat of the taper slide in a state where the valve body overlaps the taper slide in the axial direction.
The valve device according to claim 1, wherein the taper slide includes a plurality of concave portions recessed in the axial direction on the outer diameter side of the seating seat in the circumferential direction. The valve device according to claim 1,
The valve device is a valve device in which a part of a spherical surface overlaps the seat portion in the axial direction when seated on the seat. The valve device according to claim 1 or 2,
The valve device is characterized in that the concave portion is a groove extending in a radial direction or a local depression. In the valve apparatus in any one of Claims 1-3,
The recess is provided to guide the fluid flowing into the recess in the inner diameter direction,
The valve device characterized in that the side of the recess close to the seating seat is an inclined surface for directing the fluid guided in the inner diameter direction toward the fluid supply side in the axial direction. The valve device according to claim 4,
The valve device, wherein the inclined surface is a curved surface. In the valve apparatus in any one of Claims 1-5,
The valve unit, wherein the seat portion is a resin molded product obtained by molding a resin material with a molding die. In the valve apparatus in any one of Claim 1, Claim 3-Claim 6,
The valve body is an axially symmetric valve body having a conical shape or an arbitrary curved surface shape that partially overlaps the seat portion in the axial direction when seated on the seat.
The said recessed part is provided in the surface facing the said taper slide and the axial direction among the said valve bodies instead of the said taper slide, The valve apparatus characterized by the above-mentioned. The valve device according to claim 7,
The valve body is a resin molded product obtained by molding a resin material with a molding die. In the valve apparatus in any one of Claims 1-8,
The valve device characterized in that the valve driving means is an electromagnetic actuator that generates a valve opening force in accordance with an energization amount.

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